Pile driver and extractor

ABSTRACT

First and second support frames are detachably interconnected to each other by rubber torsion discs which permit resilient damping movement between the two frames. A bias weight is attached to the first frame and an eccentric weight is rotatably mounted to the second frame and driven by a hydraulic motor to develop vibratory motion. The second frame also includes first and second jaws for clamping the piling therebetween. The device is cable suspended by a crane attached to the first frame and is insulated from the vibratory motion by the torsion discs. Preferably, two eccentric weights are driven about separate shafts in counter-relative rotation synchronized out of phase to exert uniaxial vibratory force on the piling while cancelling lateral forces.

United States Patent t191 Haverkamp et al.

[11] 3,828,864 [45] Aug. 13, 1974 [54] PILE DRIVER AND EXTRACTOR [75] Inventors: Edwin Haverkamp, Grandville;

George J. Morren, Zeeland, both of Mich.

[73] Assignee: H & M Vibro, Incl., Grandville,

Mich. [22] Filed: Feb. 26, 1973 [21] Appl. No.: 335,443

[52] l U.s. ci .,173/49, 61/5`3.5, 173/112, 173/ 162 [5l] Int. Cl E02d 7/06, E02d 7/18 [58] Field of Search.; 173/49; 74/61; 175/55;

[56] References Cited v UNITED STATES PATENTS 2,695,523 ll/l954 Oswalt 74/61 3,433,3ll 3/l969 Lebelle 173/49 FOREIGN PATENTS OR APPLICATIONS 519,802 8/1953 Belgium 173/49 Primary Examiner-Ernest R. Purser Attorney, Agent, or Firm-Price, Heneveld, Huizenga & Cooper [5 7] ABSTRACT First and second support frames are detachably interconnected to each other by rubber torsion discs which -permit resilient damping movement between the two frames. A bias weight is attached to the first frame and aneccentric weight is rotatably mounted to the second frame and driven by a hydraulic motor to develop vibratory motion. The second frame also includes first and second jaws for clamping the piling therebetween. The device is cable suspended by a crane attached to the rst frame and is insulated from the vibratory motion by the torsion discs. Preferably, two eccentric weights are driven about separate shafts in counterrelative rotation synchronized out of phase to exert uniaxial vibratory force on the piling while cancelling lateral forces.

17 Claims, 8 Drawing Figures PILE DRIVER AND EXTRACTOR BACKGROUND OF THE INVENTION l. Field of the Invention This invention relates to an improved mechansim for driving and extracting elongated piling.

2. Description of the Prior Art The prior art is replete with various and sundry devices utilizing vibratory producing eccentrics in driving or extracting elongated pilings. Basically, these devices are of two types. One type in addition to the vibratory motion utilizes a driving force exerted by the supporting machinery itself such as a backhoe. The other type is crane supported by a cable and either utilizes the overall weight of the device itself or an additional dead bias weight incorporated in the vibratory mechanism itself. In either case, it is desirable to shield the-support machinery from the vibratory motion.

Generally, a mechanical spring arrangement is utilized which has proven quite dissatisfactory in that the springs tend to break or yield through overloading and- /or fatigue. The springs are relatively expensive and hence the replacement cost itself` is significant in addition to down time and ineffective operation prior to the i detection of fatigue. While a form of rubber torsion relief means has been provided in the prior art utilizing a backhoe arrangement for driving, it has not been effective to provide the necessary insulation between the vibratory mechanism and the supporting machinery itself. Also, existing arrangements utilizing a rubber torsion relief means have not been able to withstand relatively large force generations. l

A second principal drawback to many prior art arrangements is the presence of oscillating side forces created by the vibratory mechanism. The presence of side forces does not assist the driving or extracting operation and also causes side displacement problems which detract from a positive drivenl piling. A solution to this problem has been attempted in the prior art by providing pairs of driven eccentrics which are synchronized to eliminate or cancel the side forces. The devices of the prior art however have been quite complex requiring a substantially sophisticated interaction between the various eccentrics all of which has greatly added to the overall costs of these devices. The known devices which utilize a plurality of eccentrics also utilize electric motors for driving the eccentrics which require constant maintenance and individual adjustment if the vibratory force or rotational speed of the driven eccentrics are varied. The down time alone in resetting t the speed of the electric motors is quite costly.

Those devices of the prior art which utilize a dead bias weight have been unsatisfactory for several reasons. First of all, the weight required has been extremely large which not only requires excessive strength in the support thereof (and increased related costs) but also requires a correspondingly large crane or boom in the extracting phase since the dead weight must be overcome in addition to the forces exerted on the piling for withdrawing same. In many instances, the particular pilings being rdriven or extractedare positioned a considerable distance from the location of the support machinery which manipulates the vibratory mechanism and therefore a very large moment arm is created exerting arotatable force on the support machinery. The excessive weight of the known bias weights compounds the moment force exerted on the support machinery. Also, the larger the bias weight, the greater strength required in the insulation means being used.

Yet another drawback to known devices is the inability to quickly change the magnitude of the bias weight being utilized. In many installations, pilings of different size and length are driven and extracted and more economical force utilization can be realized if a particular bias weight is utilized within a given range for a given job. None of the known prior art devices provide a means for interchanging bias weights of different magnitude on the same vibratory mechanism. In light of the foregoing, there is a need in this art today for an improved pile driving and extracting device.

SUMMARY OF THE INVENTION In accordance with the invention, a pile driving and extracting device is cable supported by a crane or the like and includes a first and second support means detachably interconnected by rubber torsion means permitting resilient relative movement between the support means. A bias weight is attached to the first support means while a jaw means is attached to the second support means. A shaft is rotatably fixed to the second support means the axis of which is generally perpendicular to that of the direction of movement of the piling. An eccentric weight is mounted on the shaft and rotated about the shaft axis by a motor to develop oscillating vibratory motion in the direction of the plane of the piling.

Preferably, a pair of shafts are mounted rotatably to the second support means in a common plane generally perpendicular to the direction of movement of the piling. An eccentric weight is rotated about each shaft axis by separate hydraulic motors and synchronized out of phase to exert uniaxial vibratory force on the piling in a direction within or parallel to the plane of the piling and generally cancel vibratory forces in directions lateral to the plane of the piling. A plurality of rubber torsion discs interconnect and insulate the tirst support means from the second support means with the distortion of the discs being generally in a radial direction from the normal axis of each disc.

The unique arrangement and overall combination of the invention provides a very simplified economically constructed device which has developed a force in driving and extracting pilings which appears equal to that of existing devices of twice its magnitude in size and weight. A particular arrangement of the rubber torsion discs provides an extremely effective isolation between the vibratory mechanism and its support frame. In narrower aspects of the invention, a synchronizing mechanism is provided which assures the synchronization of the two rotating shafts and eccentric weights to avoid the build-up of lateral side vibrations. Also, a jaw means includes a clamping means which grips the piling, the latter including a hydraulically operated piston, spring biased into the non-clamping position, the piston and cylinder being supported in such a fashion that the piston is self-aligning when actuated into engagement with the piling.

The utilization of hydraulic motors greatly reduces the complexity of the motors and permits quick and easy speed adjustment by simple adjustment of the hydraulic source. The detachability of the bias weight from the second support means permits quick and easy DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a pile driver and extractor embodying the present invention;

FIG. 2 is a fragmentary front elevation view of the lower portion of the device illustrated in FIG. l;

FIG. 3 is a fragmentary front elevation view of the device illustrated in FIG. l, portions of which are in cross section;

FIG. 4 is a fragmentary side elevation view of the device illustrated in FIG. 3 taken generally along the plane of IV-IV illustrating the torsion members in both a tensioned and relaxed position;

FIG. 5 is a plan view of the clamping mechanism provided'by the invention removed from the device;

FIG. 6 is a fragmentary rear elevation view of the device illustrated iny FIGS. 1-4 illustrating the synchronizing mechanism in accordance with the invention;

FIG. 7 is a front elevation view of an alternative ernbodiment of the invention; and

v FIG. 8 is a side elevation view of the alternative embodiment illustrated in FIG. 7.v

DEscRrPrloNoF THE `PREFERRED EMBODIMENTS Referring now to the drawings in detail, FIG. 1 illustrates a cable supported pile driver and extractor 10 comprising an upper support frame 12 interconnected to a lower support frame 14 by a plurality of rubber discs 16. The entire device is supported by a cable 18 which is suspended by the boom of a crane (not shown). cable 18 is attached to a handle 20 connected to upper frame 12. A bias weight of significant weight generally on the order of 2,000-8,000 pounds is attached to upper frame 12. Preferably, upper frame I2 is filled with a lead mass 2l.

Mounted to lower frame 14 are a pair of rotating shafts 22, 22a (FIG. 6) on which are affixed respectively an eccentric weight 24, 24a. Weights 24, 24a are rotated along with shafts 22, 22a by hydraulic .motors 26, 26a (FIGS. l-4 and 6), the details of which are not described since they are conventional. That is, hydraulic motors for driving an eccentric weight rotatably about the shaft axis are well known. Referring to FIG. 2, a hydraulic fluid supply line 28 is attached to each of motors 26, 26a as well as a hydraulic fluid return line 30. Lines 28 and 30 are connected to an appropriate and conventional hydraulic fluid source and depending on the magnitudel and flow rate of the fluid supplied through line 28, the speed of motors 26, 26a can be easily varied.

As the weights are rotated, they develop vibratory forces along the general axis of plane of movement of the piling which in the illustrated drawings is vertical as shown by arrow A in FIG. 2. If weights 24, 24a are properly synchronized out of phase, lateral forces are canceled as will be described in more detail hereinafter.

A pair of jaws 32 and 34 are secured to the lower end of frame 14 and extend downwardly a distance in opposed relationship to receive'a piling or the like therebetween. A piston 36 secured in a housing 78 is movable into clamping position with a piling positioned be- .tween jaws 32 and 34 to positively clamp the piling between jaw 32 and the head of piston 36. In accordance with the invention, piston 36 is self-aligning during actuation,'the details of which will be described hereinafter.

Referring now back to FIG. l, upper support frame 12 is formed by a plurality of steel plates into a shell 40. Shell 40 has a general box-like arrangement forming side sections 42, 42a and midsection 44. the side sections 42, 42a extend downwardly beyond midsection 44 and in fact overlap lower support frame 14 while midsection 44 is spaced above lower frame I4. A pair of elongated plates 46, are attached to the front and rear face of support frame l2 each plate extending downwardly below the side portions 42, 42a. Each of the sections 42, 42a and`44 are preferably filled with lead or other substantially heavy material to provide the bias weight for driving a piling. Elongated plates 46 are utilized to attach upper frame l2 to lowerframe 14.

Lower support frame 14 is essentially in the configuration of a rectangular housing formed by a front platel 48 and a rear plate 50 interconnected to each other in a rigid conventional fashion. Support frame 14 includes a bottom plate 52 to which the jaw structure 54 is attached. The width of support frame 14 is slightly less than the spacing of sections 42, 42a of upper frame l2 while the thickness of frame 14 is less than the spacings of the pair of front elongated plates 46, and their respective rear plates so that the entire upper portion of support frame 14 in effect telescopes within the lower portion of upper frame 12. The overlapping portion of elongated plates 46 are utilized to detachably connect the lower frame to the upper frame.

The interconnection is achieved by a plurality of rubber discs 16 positioned intermediate the outer surfaces of plates 48 and 50 and the inner surfaces of elongated plates 46.

Referring to FIGS. 3 and 4, each of the rubber discs has a front and rear plate 58, 60 rigidly fixed to its front and rear ends respectively. the rear plates 60 of the discs are securely attached to plates 48 and 50 of lower support frame 14 by a plurality of bolts 62 as shown in FIG. 3. The front plate 58 is likewise secured to the inner surface of the lower portions of elongated plates 46 as illustrated in FIGS. I and 4. Thus, the jaw mechanism 54 and vibratory producing mechanism consisting of shafts 22, 22a; weights, 24, 24a and hydraulic motors 26, 26a which are interconnected to lower support frame 14 and all suspended from upper support frame 12 by the rubber discs without any rigid vibration conducting member. lt will be appreciated however that the rigidity of discs 16 is sufficient to support the entire lower support frame 14 as well as allow resilient distortion during vibration.

The vibratory operation will be described in more detail, although it will be appreciated that as the lower support frame to which the piling is affixed through jaw mechanism S4 is vibrated back and forth generally in the directions of arrow A illustrated in FIG. 2, the rubber discs will distort upwardly and downwardly as illustrated in FIG. 4. That is, the entire lower frame assembly 14 will move vertically up and down relative the upper frame assembly 12. In a driving operation, tension on cable 18 is released so that the full bias weight of upper frame l2 acts to drive the piling.

The positioning of discs 16 is such that the axis of each disc is generally perpendicular to the direction of movement of the piling. The distortion of each disc is generally along its radii which however can become quite distorted as shown in FIG. 4. In the left hand fragment of FIG. 4, the upper frame assembly 12 is illustrated in an upward deflected position (during extraction) relative lower frame 14 with the rubber disc being distorted a substantial distance relative its diameter. The right hand fragment illustrates the device in a relaxed position. The particular discs utilized encompass a rubber of substantial strength permitting distortion slightly greater than their diameter. At maximum distortion, the axis of each disc is at a substantial angle to the plane of the piling for intermittent brief moments.

The term piling is intended to include a variety of elongated structural elements which Vare commonly driven into soil both on dry land and on land which is submerged below water. The term includes items such as stakes, posts, steel sheet piling, H-bearing piling, pipe bearing piling, timber and concrete piling and pipes. The term is thus used in a broad sense and includes both hollow structural elements which are driven into the ground and later filled with poured concrete or sand as well as solid structural elements.

The device illustrated in FIGS. 1-6 is intended for heavy duty operation in driving and'extracting for example steel sheet piling exceeding 35 feet in length. The overall weight of the device is on the order of onehalf of existing devices for driving such piling and the effectiveness of its operation is to a large extent dependent on both the unique coacton of the two eccentric weights 24, 24a and the operation of rubber torsion discs 16. Since the forces required to both drive and extract 35 foot sheet pilings are quite large it has been found that pairs of vertically spaced discs 16 are required to permit generation of such forces without failure of the discs. That is, in certain job situations, vertically spaced pairs of discs are required to withstand the displacement forces acting upon the discs. The insulation provided by these multiple and vertically spaced torsion discs is extremely improved over existing devices.

Referring now to FIGS. 2 and S, the jaw mechanism 54 includes an attachment plate 68 from which `depend jaws 32 and 34. The particular configuration of jaws 32, 34 will vary depending on the particular type of piling being driven or extracted. Jaws 32, 34 illustrated are of the hairpin variety which include outward deflection portions 70 and 72 which act as a cam or guide when the jaws are being fitted over the sheet piling with the internal flat face portions 74 and 76 being generally parallel and spaced from each other approximately the width of the piling to grip the flat surfaces of the sheet.

A housing 78 likewise depends from plate 68 and forms a cover for cylinder 80 (FIG. 5) in which a piston 36 is movable in a direction generally perpendicular to the axis or plane of the piling. Piston 36 is movable through the flat portion 76 of jaw 34 toward the flat portion 74 of jaw 32 to clamp the sheeting therebetween. The piston is hydraulically actuated into clamping engagement and spring biased out of clamping engagement by a spring 82 when the hydraulic pressure is released. An extremely positive clamping force is provided on the order of 62 f tons utilizing an 8 inch clamping cylinder applying 2,500 pounds per square inch.

A particular unique feature of the clamping cylinder and piston 36 is that it lies generally loose within housing 78 so that when a clamping force is applied, the cylinder and piston are capable of slight sideways and vertical movement making piston 36 in effect selfaligning with the particular configuration of the piling. Thus, a proper clamp is always achieved eliminating the unintentional presence of superficial loading through misalignment of the clamping piston.

Plate 68 is conveniently attached to the lower plate 52 of support frame 14 by a plurality of bolts and nuts 86 clamping plates 52 and 68 together. Housing 78 has an open top for easy service of cylinder 78 and piston 36 upon removal of plate 68.

' Referring now to FIG. 6, the back side of device 10 and particularly lower support 14 is illustrated with a cover (not shown) removed exposing the synchronizing mechanism for illustration. Briefly, shafts 22 and 22a are rotatably secured between plates 48 and 50 of lower support frame 14. The shafts are mounted in a common plane generally perpendicular to the plane of the piling. An eccentric weight 24, 24a is mounted respectively to each of shafts 22, 22a and driven by separate hydraulic motors 26, 26a. It is highly desirable to synchronize the rotation of each eccentric weight 24, 24a out of phase so that the flats 90, 90a are at all times oppositely disposed to each other. In so doing, the vibratory forces generated by each eccentric in dir ections lateral to the movement of the piling are canceled while the vibratory forces generated in or parallel to the movement of the pilings are additive in a uniaxial direction producing a uniaxial force. the term uniaxial force as used herein means a cyclicly reversing force exerted along one axis, namely the axis or plane of the piling. To insure this synchronization, similar sized gears 92, 92a are mounted on the ends of shafts 22, 22a for engagement with a continuous chain 94. Since the shafts are counter-rotating relative each other, the engagement of chain 94 respectively with mesh gears 92, 92a is on opposite sides which relationship is achieved by a pair of idler gears 96 and 98 as illustrated in FIG. 6

The forces generated by the hydraulic motors in driving the eccentrics is relatively large and hence it is desirable that both motors be actuated simultaneously to reduce the strain on chain 94. The chain is engaged respectively with shafts 22, 22a essentially to maintain the relative positions of the shafts and is not provided as a drive chain to drive one of the shafts by the other. While this could be achieved, two separate drives are preferred. Experiments with the vibratory devices of the invention indicate that the rotation of eccentric weights 24, 24a independently of' each other will generally result in a self-alignment of the weights in the preferred out-of-phase synchronization. Thus, in certain installations, it may not be necessary to provide a positive synchronous control over the rotation of shafts 22, 22a. Where side vibrations of any degree are prohibited however, the positive control is preferred.

Referring to FIGS. 1, 3, 4 and 6, it will be appreciated that lower frame 14 can be quickly detached from frame l2 by simply removing the outer studs 62 at bushings 16. This permits easy replacement of an alternative upper frame having a lighter or heavier bias weight as desired. This interchangeability adds a great degree of flexibility not heretofore available in the art.

As an alternative, the mass 2l could be independently attached to frame 12 separate from the particular attachment of frame 14.

OPERATION Having described device 10 in detail, its operation should be obvious. The device is brought into proper position over a piling such as sheet steel by the manipulation of the crane and boom (not shown) from which the device is suspended by cable 18. The device is lowered with jaw mechanism 54 over the upper lip of a sheeting (not shown), the guidance being assisted by cam surfaces 70, 72 of jaws 32, 34., Preferably, the device is lowered until the upper margin of the sheeting is brought into contact with plate 68. At this point, piston 36 is charged with hydraulic fluid advancing the piston into engagement with the side of the sheeting clamping it firmly between the head of the piston and the flat portion 74 of jaw 32. The sheeting and device 10 can then be raised or positioned as desired by the operation of the crane.

In driving the sheeting, the hydraulic motors 26, 26a are preferably activated simultaneously developing a substantial vibrationin a uniaxial direction along the axis or plane A of the piling. the out-of-phase synchronization of the motors of course eliminates vibrations in lateral directions. The biased weight 21 provides the ultimate motivational force for driving the piling under vibration. Upon reaching the desired depth, the hydraulic pressure to piston 36 is released causing piston 36 to move back out of engagement with the sheet piling through the bias provided by spring 82. Tension is applied to cable 18 lifting device 10 away from the sheeting for the next operation.

Extraction of the sheeting is essentially achieved in the same fashion by first engaging and gripping the sheeting between jaws 32 and 34. Rather than immediately seeking to extract the sheeting however, it is preferred that a slightdriving force is exerted to break the sheeting loose. Thereupon, tension is applied to cable 18 as the eccentrics are rotated for withdrawal of the sheeting. v

ALTERNATIVE EMBODIMENT Referring now to FIGS. 7 and 8, an valternative arrangement of a hairpin driver and extractor 100 is illustrated. Device 100 is also cable supported by a cable 18 and includes an upper frame 12a and lower frame 14a. The device-100 is similar in many respects to that illustrated in FIGS. 1-6 and hence common elements are identified by utilizing the suffix a. The configuration of support frame 12a is somewhat different in that it is comprised of a front plate 102 and a rear plate 104 to which is securely affixed a mass of lead 106 which acts as the bias. -Plates 102 and 104 have a pair of arm like extensions 106 and 108 extending downwardly from the front and rear corners below the bias mass 106. Extensions 106 and 108 are similar to the elongated plates 46 in the embodiments of FIGS. 1-6 and are provided for attaching the upper frame assembly 12a to the lower frame assembly 14a.

The lower frame assembly 14a includes front and rear plates 110, 112 interconnected to each other in a conventional fashion. A hairpin jaw mechanism is illustrated, the details of which are not expanded upon since a variety of jaw mechanisms could be utilized including the particular unique type illustrated in the embodiment of FIGS. 1-6. In the embodiment illustrated in FIGS. 7 and 8, jaws 32a and 34a likewise include a sloped cam portion a, 72a and a flat portion 74a, 76a.

The essential difference between the embodiment illustrated in FIGS. 7 and 8 from that illustrated in FIGS. 1-6 is the use of only one vibratory mechanism comprisng a shaft and eccentric (not shown) centered with respect to the device and driven by a single hydraulic motor 116. In addition, a pair of discs 16a are utilized in both the front and rear connections between frames 12a and 14a opposed to the vertical spaced corresponding pairs in the embodiment of FIGS. 1-6. Essentially, the device is designed for lighter work situations and hence reduced materials and sizes can be appreciated. While lateral vibratory forces are not eliminated in the embodiment of FIGS. 7 and 8, in many applications, it is not necessarily required. Also, the utilization of a single rotating eccentric reduces the magnitude of forces developed as opposed to pluralities of eccentrics of similar sizes.

Again, the magnitude of bias weight 106 can be quickly changed by simply disconnecting upper frame assembly 12a from lower assembly 14a by disconnecting the bolts 118 and removing the upper support frame. An alternative bias weight can then be quickly attached to the vibratory aspect of device 100 by repositioning the newly selected upper frame assembly 12a and attaching it thereto by bolts 118.

Although but two embodiments have been shown and described in detail, it will be obvious to those having ordinary skill in this a'rt that the details of construction of these particular embodiments may be modified in a great many ways without departing from the unique concepts presented. It is therefore intended that the invention is limited only by the scope of the appended claims rather than by particular details of construction shown, except as specifically stated in the claims.

The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:

l. Apparatus for driving and extracting elongated piling in a plane comprising, in combination: first and second support means; resilient rubber torsion means interconnecting said first and second support means permitting resilient relative movement between said support means, said torsion means having spaced ends, one end of said torsion means being connected to said first support means and the other end being connected to said second support means, said torsion means having an axis extending from said one end to said other end, said axis being generally perpendicular to the driven or extracting movement of the piling in their normal relaxed position; a bias weight attached to said first support means, said first support means including means for attaching said apparatus to a boom or crane; jaw means attached to said second support means including a clamping means for clamping a piling located between said jaw means; first and second shafts rotatably fixed to said second support means and spaced from each other on opposite sides of the plane extending between said jaw means; the axes of said shafts being perpendicular to the direction of movement of the piling; an eccentric weight fixed to each of said shafts; and motor means for driving each of said eccentric weights about the axes of said shafts in counter-relative rotation out of phase to exert uniaxial vibratory force on the pilsaid piling and generally cancelling vibratory forces in directions lateral the movement of said piling.

2. Apparatus according to claim 1 wherein said rubber torsion means includes a plurality of rubber discs, each of said discs being secured at one end to said first support means and at the other end to said second support means.

3. Apparatus according to claim 2 wherein said first and second support means are partially telescoped within each other, said discs being interconnected to each of said support means within said overlapping portions.

4. Apparatus according to claim 3 wherein said second support means includes a front and rear face partially telescoped withi-n said first support means, said apparatus including at least two pairs of vertically spaced discs connected to each face of said second support means.

5. Apparatus according to claim 1 wherein said apparatus further includes a means for maintaining the synchronized counter-rotation of said eccentric weights out of phase.

6. Apparatus according to claim 5 wherein said means `for maintaining the synchronized 'rotation of said eccentric weights comprises a continuous chain in mesh engagement with sprockets mounted on each of i said shafts whereby rotation of one of said shafts illicits a corresponding synchronized rotation of the other of said shafts in the opposite direction.

7. Apparatus according to claim 1 wherein said jaw means includes first and second spaced jaws, said clamping means comprising a hydraulic actuated piston movable in a cylinder, said piston and cylinder being mounted within one of said jaws, said piston being movable in a direction gener-ally perpendicular to said piling and exerting a clamping force between the face of said piston and the other of said jaws.

8. Apparatus according to claim 7 wherein each of said jaw means includes a fiat face spaced from each other, said piston and cylinder being loosely mounted in said one jaw means whereby as said piston is actuated, said piston is self-aligning to exert a force on said piling clamped therebetween in a direction perpendicular to the face of said other jaw means.

9. Apparatus according to claim 8 wherein said clamping means includes spring means biasing said piston away from clamping engagement with a piling for releasing said piling when hydraulic pressure to said piston is removed.

l0. Apparatus according to claim 9 wherein said first and second support means are detachably interconnected.

11. Apparatus according to claim 1 wherein said motor means comprise a hydraulic motor for driving each eccentric weight.

12. Apparatus for driving and extracting elongated piling in a plane comprising, in combination: first and second support frame detachably interconnected by a plurality of resilient rubber torsion means, said torsion means insulating said first support frame from vibrations of said second support frame, said torsion means having spaced ends, one end of said torsion means being connected to said first support means and the other end being connected to said second supportmeans, said torsion means having an axis extending from said one end to said other end, said axis being generally perpendicular to the driven or extracting movement of the piling in their normal relaxed position; a bias weight attached to said first support frame, said first support frame and attached second support frame being supported by a crane or the like; jaw means extending from said second support frame for clamping a piling located generally in a plane extending between the jaw means; an eccentric mass rotatably mounted on said second support frame about an axis perpendicular to the driven or extracted direction of said piling; and a motor for driving said eccentric mass to develop uniaxial forces in the plane of said piling to drive or extract said piling.

13. Apparatus according to claim 12 wherein said rubber torsion means are discs secured at one end to said first support frame and at the other end to said second support frame.

14. Apparatus according to claim 13 wherein portions of said first and second support frames overlap, said discs being interconnected to said frames at said overlapping portions.

15. Apparatus according to claim 12 wherein said motor is a hydraulic motor.

16. Apparatus for driving and extracting elongated piling in a plane comprising, in combination: first and second support means detachably interconnected to each other, said first support means being positioned generally above said second support means, said support means including overlapping portions; resilient rubber torsion means interconnecting said first and second support means permitting resilient relative movement between said support means, said torsion means being interconnected to said support means at said overlapped portions and comprising discs positioned with their axes generally perpendicular to the directional movement of said piling when said torsion means are in their normal relaxed position; a bias weight attached to said first support means, said first support means and said attached second support means being cable supported by a crane; jaw means attached to and beneath said second support means for clamping a piling therebetween; first and second eccentric masses rotatably fixed to said second support means for rotation `about spaced axes perpendicular to the directional movement of said pilings; said eccentric masses being rotated by hydraulic motors counter-rotatably out of phase to exert uniaxial vibratory force on the piling in a direction within or parallel to the movement of said piling and generally cancelling vibratory forces in directions lateral to the movement of said piling.

17. Apparatus according to claim 16 wherein said apparatus further includes a means for maintaining the synchronized counter-rotation of said eccentric masses out of phase, said means for maintaining the synchronized counter-rotation of said eccentric masses cornprising a continuous chain in mesh engagement with means associated with said masses whereby rotation of one of said masses illicits a corresponding synchronized out of phase rotation of the other of said masses. 

1. Apparatus for driving and extracting elongated piling in a plane comprising, in combination: first and second support means; resilient rubber torsion means interconnecting said first and second support means permitting resilient relative movement between said support means, said torsion means having spaced ends, one end of said torsion means being connected to said first support means and the other end being connected to said second support means, said torsion means having an axis extending from said one end to said other End, said axis being generally perpendicular to the driven or extracting movement of the piling in their normal relaxed position; a bias weight attached to said first support means, said first support means including means for attaching said apparatus to a boom or crane; jaw means attached to said second support means including a clamping means for clamping a piling located between said jaw means; first and second shafts rotatably fixed to said second support means and spaced from each other on opposite sides of the plane extending between said jaw means; the axes of said shafts being perpendicular to the direction of movement of the piling; an eccentric weight fixed to each of said shafts; and motor means for driving each of said eccentric weights about the axes of said shafts in counter-relative rotation out of phase to exert uniaxial vibratory force on the piling in a direction within or parallel to the movement of said piling and generally cancelling vibratory forces in directions lateral the movement of said piling.
 2. Apparatus according to claim 1 wherein said rubber torsion means includes a plurality of rubber discs, each of said discs being secured at one end to said first support means and at the other end to said second support means.
 3. Apparatus according to claim 2 wherein said first and second support means are partially telescoped within each other, said discs being interconnected to each of said support means within said overlapping portions.
 4. Apparatus according to claim 3 wherein said second support means includes a front and rear face partially telescoped within said first support means, said apparatus including at least two pairs of vertically spaced discs connected to each face of said second support means.
 5. Apparatus according to claim 1 wherein said apparatus further includes a means for maintaining the synchronized counter-rotation of said eccentric weights out of phase.
 6. Apparatus according to claim 5 wherein said means for maintaining the synchronized rotation of said eccentric weights comprises a continuous chain in mesh engagement with sprockets mounted on each of said shafts whereby rotation of one of said shafts illicits a corresponding synchronized rotation of the other of said shafts in the opposite direction.
 7. Apparatus according to claim 1 wherein said jaw means includes first and second spaced jaws, said clamping means comprising a hydraulic actuated piston movable in a cylinder, said piston and cylinder being mounted within one of said jaws, said piston being movable in a direction generally perpendicular to said piling and exerting a clamping force between the face of said piston and the other of said jaws.
 8. Apparatus according to claim 7 wherein each of said jaw means includes a flat face spaced from each other, said piston and cylinder being loosely mounted in said one jaw means whereby as said piston is actuated, said piston is self-aligning to exert a force on said piling clamped therebetween in a direction perpendicular to the face of said other jaw means.
 9. Apparatus according to claim 8 wherein said clamping means includes spring means biasing said piston away from clamping engagement with a piling for releasing said piling when hydraulic pressure to said piston is removed.
 10. Apparatus according to claim 9 wherein said first and second support means are detachably interconnected.
 11. Apparatus according to claim 1 wherein said motor means comprise a hydraulic motor for driving each eccentric weight.
 12. Apparatus for driving and extracting elongated piling in a plane comprising, in combination: first and second support frame detachably interconnected by a plurality of resilient rubber torsion means, said torsion means insulating said first support frame from vibrations of said second support frame, said torsion means having spaced ends, one end of said torsion means being connected to said first support means and the other end being connected to said second support means, said torsion Means having an axis extending from said one end to said other end, said axis being generally perpendicular to the driven or extracting movement of the piling in their normal relaxed position; a bias weight attached to said first support frame, said first support frame and attached second support frame being supported by a crane or the like; jaw means extending from said second support frame for clamping a piling located generally in a plane extending between the jaw means; an eccentric mass rotatably mounted on said second support frame about an axis perpendicular to the driven or extracted direction of said piling; and a motor for driving said eccentric mass to develop uniaxial forces in the plane of said piling to drive or extract said piling.
 13. Apparatus according to claim 12 wherein said rubber torsion means are discs secured at one end to said first support frame and at the other end to said second support frame.
 14. Apparatus according to claim 13 wherein portions of said first and second support frames overlap, said discs being interconnected to said frames at said overlapping portions.
 15. Apparatus according to claim 12 wherein said motor is a hydraulic motor.
 16. Apparatus for driving and extracting elongated piling in a plane comprising, in combination: first and second support means detachably interconnected to each other, said first support means being positioned generally above said second support means, said support means including overlapping portions; resilient rubber torsion means interconnecting said first and second support means permitting resilient relative movement between said support means, said torsion means being interconnected to said support means at said overlapped portions and comprising discs positioned with their axes generally perpendicular to the directional movement of said piling when said torsion means are in their normal relaxed position; a bias weight attached to said first support means, said first support means and said attached second support means being cable supported by a crane; jaw means attached to and beneath said second support means for clamping a piling therebetween; first and second eccentric masses rotatably fixed to said second support means for rotation about spaced axes perpendicular to the directional movement of said pilings; said eccentric masses being rotated by hydraulic motors counter-rotatably out of phase to exert uniaxial vibratory force on the piling in a direction within or parallel to the movement of said piling and generally cancelling vibratory forces in directions lateral to the movement of said piling.
 17. Apparatus according to claim 16 wherein said apparatus further includes a means for maintaining the synchronized counter-rotation of said eccentric masses out of phase, said means for maintaining the synchronized counter-rotation of said eccentric masses comprising a continuous chain in mesh engagement with means associated with said masses whereby rotation of one of said masses illicits a corresponding synchronized out of phase rotation of the other of said masses. 